Power transmission mechanism



D.'M. WEIGEL 2,455,842

POWER TRANSMISSION MECHANISM Y sheets-sheet 1 Dec. 7, 1948.

' Filed March 50-I 1945 Dec.'7, 1948. D. M. wElGEL POWER TRANSMISSIONMECHANISM v 5 sheets-sheet 2 Filed March 30, 1945 Fig. 3

Dec. 7, 1948. D. M. WEIGEL POWER TRANSMISSION MECHANISM 5 Sheets-Sheet 5Filed March 30, 1945 ma. mi www m M w Patented Dec. 7, 1948 UNITEDSTATES PATENT OFFICE rovvnn 'rnnNsMIs sIoN MECHANISM Daniel M. Weigel,Detroit, Mich.

Application March 30, 1945, Serial No. v585,589

7 Claims.

IThis invention .relates broadly to power trans- Another object is toprovide a transmission in y which the lspeed ratio is automaticallyadjusted -so that the full power of input is transmitted `to the outputshaft at all speeds in the operative range.

Another object of this invention is to provide amechanism fortransmitting power 'to 'a driven .shaft from a crank pin which describesan orbit of varying magnitude. f

Further `objects .are realized by the construction of a transmissionwhich is designed to facilitate the use of a manual control mechanismfor adjustment of the speed ratio, which is .readily susceptible ofmodification of structure to accommodate various sizes and applications,and which is eiiicient and sim-ple Vof operation.

Other objects and advantages more or less ancillary to the foregoing andthe manner in which all the various objects are realized will appear inthe following description, which considered in connection with theaccompanying drawings, sets forth the preferred embodiment of theinvention.

Referring to the drawings wherein the prefer-red .embodiment of theinvention is illustrated:

Fig. 1 is a longitudinal sectional view of the improved transmission;

Fig. 2 is a transverse sectional View illustrating the .Scotch yokedrive mechanism, the section being taken online 2-2 of Fig. 1.;

Fig. 3 is a transverse section taken on line 3--3 'of Fig. l showing themanual control mechanism, the outer end of the input shaft drum .beingremoved in the interest of clarity;

Fig. 4 is a transverse sectional view taken on line .4-41 .of Fig. .1,illustrating the guide block for .supporting the drive pin within the'Scotch yke;

Fig. 5 is a View in .perspective .of the Scotch yoke; v

The invention fur- Fig. 6 is a perspective view of one of the Scotchyoke guide rollers; ,l

Fig.. 7 is a perspective view `of the input .shaft drum; Fig.. -8 is asectional view tak-en on line 8--8 of Fig. 1 showing the balance weightand `camassembly; and l l Figs. 9 and 10 yare views similar to Fig. 8illus.- trating the relation of parts in variouspositions of adjustment.

Referring first to Fig. ,1, the transmissioncom.- prises a housing lilmachined for the `seated -engagement of anti-friction bearings `II -and12. The input shaft I 3 is supported in bearingsfI'I and terminateswithin the housing in a flange I 4 formed for the support of a drum I5(see also Fig. 7) which is journalled at its opposedfend Within thebearing I2. The end of drum 15ndjacent bearing I2 is bored for thereception of a needle bearing I1 which supports the hub IB of a drivepin I9.. The axis of rotation/of the `hub within the bearing I1 iseccentric to the conrmon axis of rotation of the input shaft I3 fand thedrum I5. rA stem 20 .having a helicalgroove thereon extends -axaillyyfrom rthe -center of the hub I8 and protrudes into the'id-rum I5, thevend of said stem being .supported in -an anti-friction bearing 2I seatedon a recess `22 in the outer end `wall of said drum. i

The driving portion of pin I9 is. disposed'in normal and eccentricrelation tothe lhub I8. Rotation of the pin within the bearing Il lwilltherefore yvar-y the distance between. the aXisof the drive pin I9 andthe axisof rotationlof the input shaft |'3 and drum I5. j y As will be:seen in Figs. 1, 3 and 7 three longitudinal slots 23 are provided inthe cylindrical wall of the drum f5 to accommodate the arms 24 of -ahelix follower or nut ;25 which engages-the helica-l groove in stem 20.'The larms of the follower protrude through said'fslots and are securedto the inner race of an anti-friction .bearing l2t, the lengths ofsaidxarms 'being proportioned tosustain the bearing in concentriclrelation with the drum I5. Ayoke 21 -for shifting the follower 25 ismounted on a feed screw '2:8 supported in the housing I0. The yoke isengaged with the outer race of the bearing .216., the screw beingretained from longitudinal movement within the housing by yjam nutsengaged with the walls of the housing.- The end of the screw 2B isprovided with a worm wheel `2.9 meshed with a Worm 3!) :machined in across :shaatt Amounted inthe housing I0 :and controlled .by a handwheel'3I.

From .the foregoing it will be seen that the rotational adjustment ofthe drive pin within the pin bearings I'I is effected by rotation of thehandwheel 3|, through the agencies of the worm 30, the worm wheel 29,the screw 28, the yoke 21, the bearing 26', the helix follower 25, andthe helix in the stein 20. It will further be seen that the drum I isfree to rotate on its own axis due to the concentric relation of thebearing 26 and said drum. Y

Referring now to Figs. 1, 2, 4 and 5 the drive pin I9 .protrudes into arectangular slide frame 40 and is supported therein by a guide block 4Imounted for horizontal sliding movement within said frame. A frame guidehousing 42is secured to the face of the input shaft housing Idar-id isformed with guide rails 43 arranged to accommodate the vertical slidingmovement'of the slide frame during the rotation of the input shaft drumI5 and the drive pin I9 carried thereby.' As will be seen in Figs. 4 and5 the frame 4G is machined to support a plurality of anti-'frictionrollers It (Fig. 6) which engage the guidev rails 43.

The drive pin I9 is moved in an rorbital path by the rotation of theinput shaft, the vertical component of such motion effecting thevertical reciprocation of said frame within the guide rails, and thehorizontal component effecting the horizontal reciprocation of the guideblock 4I within the frame 40. 7

Racks 45 are mounted on the upper and lower inner faces of frame 4l] inoffset relation with each other and normal to the medial axis of pin I9.The portion of pin I9 adjacent said racks is provided with a wearbushing 45 inserted in a pilot bearing 41 formed in the end of clutchshaft 4g. The outer surface of said clutch shaft is machined withlongitudinal grooves 49 to facilitate the pivotal support of a pluralityof overrunning clutch pawls 50. Tangential springs 5I are provided foreach group of contiguous pawls to maintain contact between the frictionfaces of said pawls and the inner surface of a rack pinion 53constituting a clutch drum.

As Awill ybe seen in Fig. l, the inner end of the shaft 48 is providedwith a pair of pinions entrained respectively with the racks '45, eachpinion operating a separate series of clutch pawls 50. Since each pinionis meshed with one rack only, the horizontal reciprocation of the pin I9will effectuate a rotary oscillation of said pinions about the clutchshaft A48, the rotation of each pinion opposing the movement of theother. The oscillation of the pinions is translated into unidirectionalrotation of clutch shaft 48 by the ratchet action of the clutch pawls50. This type of overrunning clutch mechanism is the subject of my priorPatent No. 2,240,359.

A second housing 60 is bolted tothe frame guide housing 42, and isprovided with seats for the anti-friction bearings 6I and 62 in theopposed ends thereof, which, as shown, may be arranged in concentricrelation with the axis of the input shaft Il. A plate B3 is journalledin the bearings 6I adjacent the frame guide 42, said plate having aneccentric hole 64 therethrough for the reception of pin bearings 65which support 'a balance weight cam 65. The clutch shaft lill isjournalled in an eccentric hole in the balance cam and terminates withinthe housing t!) in an enlarged splined portion 6l engaged with auniversal joint 68. The eccentricity of the hole .94 in plate 63 isequal to that of the seat I6 in the drum l5; likewise the center tocenter distance between the pin I 9 and the hub I8 is equalto theydistance between the shaft 48 and the hole 64 in the balance weight cam65. Thus the rotary adjustment of the pin I9 as initiated by thehandwheel control will effectuate a similar adjustment of the balanceweight cam 56 Within the plate 63.

As seen in Figs. 1, 8, 9 and l0 a balance plate 69 is journalled on thecam E6 and controlled thereby. A pin or bolt is mounted in the plate 53adjacent the outer edge thereof and protrudes through a radial slot ilin the balance weight 59 to effect the rotation thereof in unison withthe plate.

The universal joint 68 is coupled with a shaft T3 having a sp-lined endportion 'I4 thereon for sliding engagement within a broached sleeve I5on a second universal joint 1t. A driven shaft l1 is supported in thebearings S2 and keyed to the universal joint 16.

Figs. 8, 9 and 10 illustrate the range of adjustment of the speed ratioof the mechanism, Fig. 8 showing the position of the parts during theoptimum output speed of the device, Fig. 9 an intermediate position, andFig. 10 the position in which no drive Ais effected. It will be notedthat this adjustment may be eifected by the handwheel control asheretofore described or by the governing action of the balance weightwhich opposes the weight of the revolving pin assembly.

In the latter case the manual control mechanism may either bedisconnected or entirely eliminated from the structure. The operativecharacteristics of the governor action transmission are such that theoutput shaft revolves at the maximum speed consonant with the torqueimposed thereon so that full power is transmitted at all speeds.

In operation, when the drive pin I9 is adjusted at a fixed distance fromthe axis of the input shaft, the drum I5 will rotate about its axismoving the pin I9 in an orbital path of movement. The shaft 48 and theuniversal joint 68 will follow a similar orbit, and the shaft I3 willmove in a conical path having its apex at the center of the outeruniversal joint 15. The amplitude of the oscilation of pinions 53 isdependent upon the extent of horizontal translation thereof within theslide frame 4ll which is, in turn, determined by the orbital radius ofthe drive rin I9. Hence the speed of rotation imparted to the shaft 49by the overrunning clutches is biased by the speed of the input shaftand the position of adjustment of the drive pin.

Although the foregoing description is necessarily of a detailedcharacter, in order 'that the invention may be completely set forth. itis to be understood that the specific termirology is not intended to berestrictive, and that various rearrangements of parts and modificationsof detail may be resorted to without departing from the scope or spiritof the invention as herein claimed.

I claim:

l. A power transmission comprising a housing, a drive shaft journalledtherein, an enlarged inner end on said shaft having an eccentric recesstherein, a drive pin hub journalled in said recess, a drive pin thereonin eccentric relation therewith, a clutch shaft journalled on said pin,a pinion journalled on the clutch shaft, a slide frame circurnambientsaid pinion and mounted for reciprocative movement within the housing, agear rack in said frame engaged with said pinion, overrunning clutchpawls intermediate said pinion and said clutch shaft, a plate having aneccentric hole therethrough mounted for rotative movement in saidhousing, an eccentric cam journalled in said hole, a balance Weightmounted on said cam, an eccentric bearing in said cam for the support ofthe clutch shaft, a driven shaft and articulate linkage intermediate theclutch shaft and the driven shaft.

2. A transmission comprising a housing, a drive shaft journalledtherein, an eccentric bearing on the inner end of said shaft, a drivepin carried thereby, the driving portion of said pin being in eccentricrelation to said bearing, a frame mounted for sliding movement withinsaid housing, gear racks mounted in opposed staggered relation with eachother in said frame, a clutch shaft journalled on the drive pin, pinionsjournalled on the clutch shaft and meshed with said racks, clutchelements intermediate said clutch shaft and said pinions for effectingunidirectional rotation of said shaft, a balance plate mounted in weightopposition to said drive pin, a driven shaft and linkage intermediatesaid clutch shaft and said driven shaft.

3. A power transmission embodying a housing, a drive shaft therein, aclutch shaft, an eccentric drive pin on said drive shaft journalled inthe end of said clutch shaft, means for varying the eccentricity of thedrive pin, clutch pawls pivotally supported on the clutch shaft, pinionson said shaft engaged by said pawls, a Scotch yoke surrounding saidpinions, gear racks therein entrained respectively with said pinions,said racks being substantially parallel and on opposite sides of saidclutch shaft, a fly Weight mounted to rotate in unison with said drumand to oppose the Weight of the drive pin and clutch shaft, universaljoints coupled with said clutch shaft and a driven shaft coupledthereto.

4. A transmission comprising a drive shaft having an eccentric openingin the inner end thereof, a drive pin journalled in said openingeccentric thereto, a clutch shaft journalled on said pin, overrunningclutches on said shaft, pinions in driving relation to the saidclutches, a Scotch yoke disposed in transaxial relation with said shaft,racks therein intermeshed with said pinions, a bearing support for saidshaft adjacent said pinions, a driven shaft, and driving connectionsfrom said clutch shaft to said driven shaft.

5. A transmission comprising a housing, a drive shaft journalledtherein, a bearing cage mounted on said shaft within said housing, saidcage having a bore in the end thereof eccentric the medial axis of saidshaft, a drive pin, an eccentric hub thereon journalled in said bore, aclutch shaft having an axial bore therein journalled on said pin,pinions on said clutch shaft, unidirectional clutches thereinoperatively engaged with said clutch shaft, a Scotch yoke mounted insaid housing, racks therein engaged with said pinions, a disc having aneccentric opening therein journalled in said housing, a plate journalledin said opening, said plate having an eccentric hole thereinconstituting a journal bearing for said clutch shaft, a slidablecounterbalance Weight on said plate, a universal joint on said clutchshaft and an output shaft driven thereby.

6. A transmission comprising a housing, a drive shaft journalledtherein, a bearing member having an eccentric bore in the end thereofmounted on said shaft, a rectangular frame mounted 0n said housing, asecond rectangular frame mounted for vertical reciprocation in the rstnamed frame, a third frame mounted for horizontal reciprocation in thesecond named frame, a drive pin, an eccentric hub thereon journalled inthe eccentric bore in said bearing member, a clutch shaft journalled onsaid drive pin, a pair of pinions mounted on said clutch shaft in sideby side relation, racks in the top and bottom rails of the second namedframe enmeshed respectively with said pinions, overrunning clutches insaid pinions engaged with said clutch shaft, means to vary the magnitudeof the path of movement of said clutch shaft as guided by said secondand third named frame, and an output shaft driven by said clutch shaft.

7. A transmission comprising a housing, a drive shaft journalledtherein, said shaft having an eccentric bore in the end thereof, a drivepin, an ec centric hub thereon journalled in the eccentric bore in saidshaft, a clutch shaft journalled on said drive pin, means on said hub tovary the eccentricity of the drive pin relative to the drive shaft, aScotch yoke operatively connected with said clutch shaft, an overrunningclutch on said clutch shaft, means associated with the Scotch yoke andoverrunning clutch to rotate said clutch shaft, a universal joint onsaid clutch shaft and an output shaft driven thereby.

DANIEL M. WEIGEL.

REFERENCES CITED The following references are of record in the file ofthis patent:

UNITED STATES PATENTS Number Name Date 685,834 Green Nov. 5, 19011,234,455 Fox July 24, 191'7 1,572,360 Petersson Feb. 9, 1926 1,996,938Svensson 1 Apr. 9, 1935 2,005,227 Johnson June 18, 1935 2,036,624Garratt Apr. 7, 1936 2,036,625 Garratt Apr. 7, 1936

